CN111339628B - Fluid-solid coupling-based high-speed railway wheel rail area vibration and noise analysis method - Google Patents
Fluid-solid coupling-based high-speed railway wheel rail area vibration and noise analysis method Download PDFInfo
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Abstract
The invention provides a fluid-solid coupling-based method for analyzing vibration and noise of a wheel track area of a high-speed railway. The method comprises the following steps: calculating wheel-rail interaction force according to vibration admittance and joint roughness of wheels, steel rails and wheel rails of the high-speed railway, constructing a wheel-rail vibration noise joint prediction model based on fluid-solid coupling, and predicting by using the wheel-rail vibration noise joint prediction model to obtain vibration noise of the wheels, the steel rails and a rail plate; obtaining aerodynamic pressure in a flow field by using a fluid domain model of the flow field in the wheel rail area, and simulating according to the aerodynamic pressure to obtain aerodynamic noise in the wheel rail area; according to vibration noise of wheels, steel rails and track plates and aerodynamic noise of a wheel rail area, near-field noise and far-field noise of the wheel rail area are analyzed on the basis of a fluid-solid coupling theory. The method analyzes the vertical and longitudinal transfer characteristics in the ballastless track vibration frequency domain by using a harmonic response analysis method, and realizes the joint analysis of the vibration and noise analysis of the wheel track area of the high-speed railway.
Description
Technical Field
The invention relates to the technical field of characteristic analysis of vibration and noise of high-speed railways, in particular to a method for analyzing vibration and noise of a high-speed railway wheel rail area based on fluid-solid coupling.
Background
The high-speed railway plays a great role in meeting the passenger demand of China and promoting economic development by virtue of the advantages of high smoothness, high stability, high timeliness and the like. In China, the state railway administration defines China high-speed railway as a passenger train special line railway with the designed running speed per hour of more than 250 kilometers and the initial operating speed per hour of more than 250 kilometers. With the continuous improvement of the living standard of people in China, the requirements of people on the living quality are continuously improved, and new requirements and new targets are provided for noise control and prevention of high-speed railways. Therefore, scientific and reasonable characteristic analysis of the vibration and noise of the high-speed railway is required.
At present, in the research on the wheel-rail vibration and noise characteristic numerical analysis of the high-speed railway in the prior art, a fixed-value wheel-rail force is mainly adopted or a fixed-point wheel-rail force frequency spectrum is obtained through conversion based on a relative force excitation model and is used as the disturbance of the vibration noise of a track structure. The method does not consider the coupling effect of the vehicle and the track, and only can be used for analyzing the inherent frequency domain transfer characteristic of the wheel track system, but cannot obtain the characteristic of wheel track vibration noise caused by the actual passing of a high-speed train. At present, the noise of a wheel track area is researched, or only the vibration noise is analyzed and researched by a related theoretical test, or only the pneumatic noise is taken out independently for noise characteristic analysis, so that the integrity of the noise analysis of the wheel track area is broken by force. Therefore, the existing wheel-rail vibration and noise analysis method has the defects.
Disclosure of Invention
The embodiment of the invention provides a fluid-structure interaction based method for analyzing vibration and noise in a wheel rail area of a high-speed railway, which aims to solve the problem that the vibration and noise characteristics caused by actual passing of a high-speed train cannot be analyzed due to the adoption of a fixed-value wheel rail force in the prior art.
In order to achieve the purpose, the invention adopts the following technical scheme.
A method for analyzing vibration and noise of a high-speed railway wheel rail area based on fluid-solid coupling comprises the following steps:
calculating wheel-rail interaction force according to vibration admittances and combined roughness of wheels, steel rails and wheel rails of the high-speed railway, constructing a wheel-rail vibration noise combined prediction model based on fluid-solid coupling according to the wheel-rail interaction force, and predicting to obtain vibration noise of the wheels, the steel rails and the track slabs by using the wheel-rail vibration noise combined prediction model;
constructing a fluid domain model of a wheel rail area flow field, obtaining aerodynamic pressure in the flow field by using the fluid domain model, and simulating according to the aerodynamic pressure to obtain aerodynamic noise of the wheel rail area;
and according to the vibration noise of the wheels, the steel rails and the track plate and the aerodynamic noise of the wheel rail area, performing sound source contribution analysis on the near-field noise and the far-field noise of the wheel rail area based on the fluid-solid coupling theory.
Preferably, the method for calculating the vibration admittance of the wheel, rail and wheel rail comprises:
by applying a force F to a point j on the rail and wheel respectivelyiCalculating the displacement response D of the wheel and the steel rail at the loading point by using a harmonic response analysis methodjVibration admittance at wheel and rail loading points
Calculated by the following formula, respectively:
wheel-rail contact admittance alphacontactFor wheel-rail contact rigidityKcontactThe reciprocal of (a), namely:
αcontact＝1/Kcontact (3)
preferably, the wheel-track vibration noise combined prediction model adopts finite element analysis software to select a ballastless track for modeling, a steel rail is simulated by adopting a three-dimensional solid unit, a fastener system is simulated by adopting a spring damping unit, a track plate is simulated by adopting a three-dimensional solid unit, the wheel-track vibration noise combined prediction model comprises a steel rail and a half track plate, and boundary conditions are simulated by applying symmetrical constraint at the middle part of the track plate and performing full constraint at the structural joint of the lower track plate.
Preferably, the constructing a fluid domain model of the wheel-track area flow field includes:
establishing a fluid domain model with the radius of 4.25m on the lowest axis of a symmetrical surface at one end of a foundation below a concrete base, completely removing a wheel body, a steel rail, a track plate, the base and the foundation below the base in the fluid domain by using Boolean operation, only leaving a pure fluid domain model, leading out the outer surface of the fluid domain model, carrying out grid division, and dividing the grid of the outer surface into an inlet surface, an outlet surface, symmetrical side surfaces, a top surface and a bottom surface, the minimum mesh size of the inlet face, the outlet face and the symmetrical side face is 0.01m, the mesh type is triangular, the minimum grid size of the top surface and the bottom surface is 0.5m, the grid type is triangular, the minimum grid size of the grid division of the air contact surface of the steel rail and the wheel is 0.01m, the grid type is triangular, and the 3D body grid division is performed based on the grid division of the outer surface of the fluid domain model and the grid division of the air contact surface of the steel rail and the wheel.
Preferably, the obtaining of aerodynamic noise of a wheel rail region according to the aerodynamic pressure simulation includes:
constructing an air domain prediction model of the aerodynamic noise, introducing aerodynamic pressure in a flow field under a frequency domain into the air domain prediction model of the aerodynamic noise, and simulating to obtain the aerodynamic noise of a wheel track region;
the construction of the air domain prediction model of the aerodynamic noise comprises the following steps: selecting a turbulence model, selecting air by default for a fluid material, selecting corresponding flow surfaces at an inlet, an outlet, a bottom, an upper part and a boundary which are arranged in the prior art, and dividing grids, wherein the type of an inlet boundary condition selects a speed inlet, the speed is selected according to the actual driving speed, the type of an outlet edge selects a pressure outlet, on a symmetrical surface of the model, the type is selected and set as a symmetrical boundary, the types of boundary conditions on other surfaces are set as boundary surfaces which can not be passed by fluid, after the setting is finished, a pressure correction algorithm based on a pressure method is selected for solving, the calculation step length is selected according to 1/2 with the highest analytical frequency reciprocal, and a time domain result under the aerodynamic pressure in the flow field is obtained after the calculation is finished; .
Performing FFT on the time domain result under the aerodynamic pressure to obtain the aerodynamic pressure in the flow field under the frequency domain;
pneumatic pressure p in the frequency domain for each point i in the air domainiAerodynamic noise N from each pointiThe correlation between them is as follows:
preferably, the sound source contribution analysis is performed on the near-field noise and the far-field noise of the wheel rail area based on the fluid-solid coupling theory according to the vibration noise of the wheel, the steel rail, the track slab and the aerodynamic noise of the wheel rail area, and includes:
the near-field noise is obtained by extracting air pressure values at all nodes in the air domain and converting the air pressure values, the far-field noise is based on an algorithm of acoustic infinite elements and numerical interpolation, and the air pressure p corresponding to an infinite element grid unit j generated on the outermost surface of the air domain is obtained according to the calculation result of the near-field noisejThe calculation is carried out in such a way that,
the distance from each point i in the region outside the air domain to the position of the mass center is obtained by setting the position of the mass center of a geometric body formed by an infinite element closed surfacerSelecting a suitable infinite element boundary interpolation order n, and calculating according to the following formula to obtain the air corresponding to the infinite element grid unit j generated on the outermost surface of the air domainPressure pj：
Preferably, the sound source contribution analysis of the near-field noise and the far-field noise in the wheel rail area based on the fluid-solid coupling theory according to the vibration noise of the wheel, the steel rail and the track slab and the aerodynamic noise in the wheel rail area includes:
for near-field noise analysis of a wheel track area, under the running speed of each train, 8 observation points are placed for observing the noise change value of the train, each observation point is provided with a microphone, and the 8 observation points are arranged beside a line; the measuring points 1 and 2 are based on the requirement of GB/T5111 plus 2011 for the placement of the position of an acoustic noise measurement microphone for the emission of a rail locomotive, the microphone is placed 7.5m away from a steel rail and 1.2m +/-0.2 m above the top surface of the steel rail, the observing points 1 and 2 are environment evaluation index measuring points, A weighting sound pressure levels at different train running speeds are respectively adopted for noise evaluation at two points, the four points of the measuring points 3, 4, 5 and 6 are observation points which are transversely 1m away from the central axis of the two rails and are positioned on the same cross section, on the vertical height, the measuring point 3 is 0.976m away from the bottom surface of the steel rail, the measuring point 4 is 0.576m away from the bottom surface of the steel rail, the measuring point 5 is 0.176m away from the bottom surface of the steel rail, namely on the height of the top surface of the rail, the measuring point 6 is 0.088m away from the bottom surface of the steel rail, namely on the height of the rail waist surface, and the measuring points 7 and 8 are two observation points 0.176m away from the bottom surface of the longitudinal steel rail, namely on the height of the top surface of the rail, the observation point 5 is also positioned on the plane, and the horizontal distance of the observation point 7 is 7.5m away from the central axis of the two rails and is on the same longitudinal plane as the ring evaluation point 1; the horizontal distance of the observation point 8 is 1.5m away from the rail, and the observation point and the ring evaluation point 2 are on the same longitudinal plane; the observation points 5, 7 and 8 form a group of points for observing the change condition of the measuring point noise of the transverse section at different train running speeds.
According to the technical scheme provided by the embodiment of the invention, the vertical and longitudinal transfer characteristics of the ballastless track in the vibration frequency domain can be analyzed by establishing the wheel-rail vibration finite element model of the ballastless track of the high-speed railway and using a harmonic response analysis method. The method realizes the combined analysis of the vibration and noise analysis of the high-speed railway wheel rail area, makes up the defects of the single vibration, vibration noise or air noise characteristic analysis in the past, and provides a more scientific and reasonable method for the analysis of the vibration and noise of the high-speed railway.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the description below are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic diagram illustrating an implementation principle of a fluid-solid coupling-based method for analyzing vibration and noise in a wheel track area of a high-speed railway according to an embodiment of the present invention;
FIG. 2 is a processing flow chart of a method for analyzing vibration and noise in a wheel track area of a high-speed railway based on fluid-solid coupling according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a high-speed railway wheel-rail vibration noise joint prediction model provided by an embodiment of the invention;
fig. 4 is a schematic diagram of a fluid domain model of a wheel track area flow field according to an embodiment of the present invention;
FIG. 5 illustrates a rail vibration displacement admittance at the mid-span of a two-fastener in accordance with an embodiment of the present invention;
FIG. 6 is a schematic diagram of a selected position of a noise measurement point according to an embodiment of the present invention;
FIG. 7 is a weighted sound pressure level of vibration noise A of the measuring point 1 according to the embodiment of the present invention;
fig. 8 is a weighted sound pressure level of vibration noise a at measuring point 2 according to an embodiment of the present invention;
FIG. 9 is a graph illustrating the sound pressure level of the vibration noise at an octave of the vertical plane 1/3 according to an embodiment of the present invention;
FIG. 10 is a cross-sectional view of a horizontal plane 1/3 octave vibration noise sound pressure level provided by an embodiment of the present invention;
FIG. 11 is a pneumatic noise A weighting sound pressure level of a measuring point 1 according to an embodiment of the present invention;
FIG. 12 is a pneumatic noise A weighting sound pressure level of the measuring point 2 according to the embodiment of the present invention;
FIG. 13 is a graph showing an 1/3 octave aerodynamic noise sound pressure level along a vertical plane according to an embodiment of the present invention;
FIG. 14 is a cross-sectional view of a lateral plane 1/3 octave aerodynamic noise sound pressure level provided by an embodiment of the present invention;
FIG. 15 shows the contribution of each structural vibration noise source at point 1 at a speed of 250km/h according to an embodiment of the present invention.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are exemplary only for explaining the present invention and are not construed as limiting the present invention.
As used herein, the singular forms "a", "an", "the" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and/or "comprising," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. It will be understood that when an element is referred to as being "connected" or "coupled" to another element, it can be directly connected or coupled to the other element or intervening elements may also be present. Further, "connected" or "coupled" as used herein may include wirelessly connected or coupled. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.
It will be understood by those skilled in the art that, unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the prior art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
For the convenience of understanding of the embodiments of the present invention, the following detailed description will be given by way of example with reference to the accompanying drawings, and the embodiments are not limited to the embodiments of the present invention.
At present, the connection between the wheel track vibration and the gas vibration noise is not clearly known at home and abroad, so that the vibration of the wheel track area of the ballastless track of the high-speed railway, the time-frequency characteristics of the noise and the contribution proportion of a noise source need to be deeply researched and analyzed, a method for analyzing the vibration and the noise of the wheel track area of the high-speed railway based on fluid-solid coupling is established, and theoretical support is provided for the formulation and optimization of control measures for noise pollution of the ballastless track of the high-speed railway and the evaluation of the noise environment of a railway system.
Fig. 1 is a schematic diagram illustrating an implementation principle of a method for analyzing vibration and noise in a wheel rail area of a high-speed railway based on fluid-structure interaction according to an embodiment of the present invention, where a specific processing flow is shown in fig. 2 and includes the following processing procedures:
step S210, calculating wheel-rail interaction force according to vibration admittances and joint roughness of wheels, steel rails and wheel rails of the high-speed railway, establishing a wheel-rail vibration noise joint prediction model based on fluid-solid coupling according to the wheel-rail interaction force, and predicting by using the wheel-rail vibration noise joint prediction model to obtain vibration noise of the wheels, the steel rails and the track slabs.
The method is developed from the aspects of pneumatic noise and vibration noise. And for vibration noise, establishing a wheel-rail vibration analysis model based on the similarity theory, the interface mechanics, the finite element theory and the like. Calculating the wheel-rail interaction force through the obtained vibration admittance and the joint roughness of the wheel, the steel rail and the wheel rail,
respectively establishing a space finite element model comprising wheels, steel rails, a track structure and a lower foundation based on a finite element method, and respectively applying an acting force F to a certain point j on the steel rails and the wheelsjCalculating the displacement response D of the wheel and the steel rail at the loading point by using a harmonic response analysis methodjVibration admittance at wheel and rail loading points
Calculated by the following formula, respectively:
wheel-rail contact admittance alphacontactFor wheel-rail contact stiffness KcontactThe reciprocal of (a), namely:
αcontact＝1/Kcontact (3)
the calculation formula of the wheel-rail interaction force is as follows:
therefore, the vibration response conditions of the wheels, the steel rails and the track plates are researched. And then establishing a high-speed railway wheel-track vibration noise combined prediction model by means of finite element-boundary element coupling, numerical analysis and the like based on wheel-track coupling dynamics and fluid-solid coupling theory. And for the vibration noise of the wheel, the steel rail and the track plate obtained through prediction and the combined vibration of the wheel, the steel rail and the track plate, the characteristics and the change rule of the vibration noise of the ring evaluation point, the vertical plane measurement point and the transverse plane measurement point in the wheel rail area are researched.
Step S220, establishing a fluid domain model of the wheel track area flow field, obtaining aerodynamic pressure in the flow field by using the fluid domain model, and simulating according to the aerodynamic pressure to obtain aerodynamic noise of the wheel track area.
For aerodynamic noise, based on aerodynamic acoustics, flow-induced vibration theory, vortex sound theory and the like, a fluid domain model of a wheel rail area flow field is established, for the convenience of setting boundary conditions in aerodynamic noise calculation, the outer surface of the fluid domain model is led out and subjected to grid division to be respectively an inlet surface, an outlet surface, symmetrical side surfaces, a top surface and a bottom surface, because the inlet surface, the outlet surface, the top surface and the side surfaces are close to a steel rail, the calculation influence on the aerodynamic noise is large, the grid division is as small as possible, and the grid size of an air domain is ensured to be smaller than the sound velocity v divided by the highest analysis frequency fmaxOne tenth to one twentieth of the value.
And constructing an air domain prediction model of the aerodynamic noise, introducing aerodynamic pressure in a flow field under a frequency domain into the air domain prediction model of the aerodynamic noise, and simulating to obtain the aerodynamic noise of the wheel track region.
The construction of the air domain prediction model of the aerodynamic noise comprises the following steps: selecting a reasonable turbulence model (such as large vortex simulation, proportional vortex and the like), selecting air as a default for a fluid material, selecting corresponding flow surfaces at an inlet, an outlet, a bottom, an upper part and a boundary which are arranged in the prior art, and dividing a grid, wherein a speed inlet (velocity-inlet) is selected according to the type of an inlet boundary condition, and the speed is selected according to the set train running speed and the actual running speed, such as 250km/h, 300km/h, 350km/h, 400km/h and the like; an outlet-side type selection pressure outlet (pressure-outlet); on the symmetry plane of the model, the type selection is set as a symmetry boundary (symmetry); and the boundary condition types on the other faces are set as boundary faces (walls) through which the fluid cannot pass. And after the setting is finished, a pressure correction algorithm based on a pressure method is selected for solving, the calculation step length is selected according to 1/2 of the reciprocal of the highest analysis frequency, if the highest analysis frequency is 5000Hz, the sampling step length is 0.0001s, and a time domain result under the aerodynamic pressure in the flow field is obtained after the calculation is finished.
And then the time domain result under the aerodynamic pressure is subjected to FFT to obtain the aerodynamic pressure in the flow field under the frequency domain. And constructing an air domain prediction model of the aerodynamic noise, introducing the aerodynamic pressure in the flow field under the frequency domain into the air domain prediction model of the aerodynamic noise, and simulating to obtain the change condition of the aerodynamic noise, namely obtaining the aerodynamic noise of the wheel track area.
Pneumatic pressure p of points i in the air fieldiAerodynamic noise N from pointsiThe correlation between them is as follows:
and further researching the characteristics and the change rule of the aerodynamic noise of the wheel rail area at a ring evaluation point, a vertical plane measurement point and a transverse plane measurement point.
And S230, performing sound source contribution analysis on the near-field noise and the far-field noise of the wheel track area of the high-speed railway based on the fluid-solid coupling theory according to the vibration noise of the wheels, the steel rails and the track plate and the aerodynamic noise of the air of the wheel track area.
The near-field noise is obtained by extracting air pressure values at all nodes in the air domain and converting the air pressure values, the far-field noise is based on an algorithm of acoustic infinite element and numerical interpolation, and firstly, the air pressure p corresponding to an infinite element grid unit j generated on the outermost surface of the air domain is obtained according to a near-field calculation resultjCalculating to obtain the distance from each point i in the region outside the air region to the centroid position by setting the centroid position of the geometric body formed by the infinite element closed surfacerAnd calculating the air pressure distribution condition of each point i outside the air domain according to the following formula by selecting a proper infinite element boundary interpolation order n:
and calculating the sound pressure value of the point by using the formula 4 according to the obtained air pressure value.
A schematic diagram of the high-speed railway wheel-track vibration noise joint prediction model in step S210 is shown in fig. 3, and finite element analysis software is adopted to select a fragment of ballastless track with a length of 6.5m for modeling, a steel rail is simulated by using a three-dimensional solid unit, a fastener system is simulated by using a spring damping unit, and a track plate is simulated by using a three-dimensional solid unit. By using symmetry, the finite element model only comprises one steel rail and half track slabs, and boundary conditions are simulated by applying symmetric constraint at the middle part of the track slabs and performing full constraint at the structural nodes of the lower track slab.
When wheel-rail interaction forces are applied, the wheel and rail are coupled to each other through dynamic forces at the rail contact interface. Firstly, by referring to relevant specifications and documents, determining a track roughness spectrum r (w) required to be adopted in prediction, wherein ω -2 π upsilon/λ is excitation fillet frequency, v is vehicle speed, and λ is roughness spectrum wavelength, then the dynamic wheel-track acting force can be expressed as:
in the formula: fCThe dynamic acting force of the wheel track, r is the wheel track combination roughness spectrum after considering the contact filtering effect of the wheel track, alphaW、αC、αRRespectively wheel admittance, wheel-rail vertical contact spring admittance and wheel-rail contact position track system admittance. The wheel-rail acting force is respectively applied to the contact point positions of the steel rail and the wheel, and the dynamic response including displacement, speed and acceleration at each node of the wheel and the rail is calculated by utilizing the established wheel and rail space dynamics model.
Results obtained by simulation
The relevant track structure parameters selected by the wheel-track vibration noise joint prediction model are shown in the following table:
the main key point of the gridding of the established model is to control the gridding quality and quantity of the finite element model at the applied load position, namely the wheel and the steel rail, and the gridding of the fastener, the track plate and the lower structure is not required to be so fine, so that the computer resource consumption is saved, the gridding quality and quantity of the finite element model at the applied load position, namely the wheel and the steel rail, are controlled, and the functional structure characteristics of the plate-type ballastless track can be better considered for the fastener model calculation time. The whole wheel model is discretized into 92673 nodes, 479352 unit grids are in total, the steel rail model is discretized into 25125 nodes, 17800 unit grids are in total, and the quality requirement of vibration analysis response is met. On the basis of a vibration analysis model, according to the requirement of the maximum cell size of the model, the maximum cell size of the boundary meta-model is not larger than 0.012m, and an acoustic radiation noise model is established.
Fig. 4 is a schematic diagram of a fluid domain model of a wheel-rail region flow field according to an embodiment of the present invention, where a fluid domain model with a radius of 4.25m is established on a lowermost axis of a symmetric plane at one end of a foundation below a concrete base, and a boolean operation is applied to completely omit a wheel body, a steel rail, a rail plate, a base and the foundation below the base in the fluid domain, so that only a pure fluid domain model is left. The outer surface of the fluid domain model is led out and subjected to grid division, and the fluid domain model is respectively an inlet surface, an outlet surface, a symmetrical side surface, a top surface and a bottom surface, because the inlet surface, the outlet surface, the top surface and the side surface are close to a steel rail, the calculation influence on pneumatic noise is large, the grid division is as small as possible, the minimum grid size on the surface is 0.01m, the grid type is triangular, other surfaces save calculation resources, only the minimum grid size is 0.5m, and the grid type is triangular. For the mesh division of the air contact surface of the steel rail and the wheel, the minimum mesh size on the surface is 0.01m, the mesh type is triangular, and the 3D volume mesh division is carried out on the basis of the established boundary surface of each fluid domain aerodynamic noise and the combination of the established air contact surface on the outer surface of the steel rail wheel.
Fig. 5 is a schematic view of the rail vibration displacement admittance at the midspan of two fasteners according to an embodiment of the present invention, as shown in fig. 5, a unit of simple harmonic load is applied to the rail, where the excitation point is above the middle of the two fasteners. And calculating the vibration displacement response of the steel rail by utilizing a harmonic response analysis function, respectively extracting displacement admittance results of the rail top of the steel rail at the intervals of 1, 2 and 3 fasteners from the excitation point, and analyzing the transmission characteristic of the vibration of the steel rail along the longitudinal direction. Viewed on the whole, the amplitude of the displacement admittance of the steel rail is continuously reduced along with the increase of the frequency; and along the rail is vertical, along with the continuous increase of distance from the excitation point, the displacement admittance amplitude of the rail top of the rail has certain gradual attenuation, and it can be obviously seen that the vibration of the rail is obvious along the vertical attenuation when the frequency is low, and the vibration of the rail is less along the vertical attenuation when the frequency is high.
Based on the vibration displacement response results of the wheel rail system under the train running speeds of 200km/h, 250km/h, 300km/h and 350km/h, the sound pressure levels of the measuring points at different heights and different distances in the sound field of the wheel rail peripheral area under various train running speeds, the 1/3 octave sound pressure level and the A weighting sound pressure level are respectively subjected to statistical analysis. For near-field noise analysis of a wheel track area, 8 observation points are arranged at the running speed of each train for observing the noise change value of the train, and the arrangement positions of the 8 observation points beside a line are shown in fig. 6. Wherein, the measuring points 1 and 2 are based on the general requirement of GB/T5111-2011 on the position placement of the acoustic measurement microphone for the emission noise of the rail locomotive, and the microphone is placed 7.5m away from the steel rail and 1.2m +/-0.2 m above the top surface of the rail. The measuring point 1 is an observation point which is 1.376m higher than the bottom surface of the steel rail and 7.5m away from the steel rail in the transverse direction, and the measuring point 2 is an observation point which is 1.376m higher than the bottom surface of the steel rail and 1.5m away from the central axis of the two rails in the transverse direction. Noise observation points 1 and 2 are environment evaluation index measurement points, noise evaluation is carried out on two points by respectively adopting A weighting sound pressure levels under different train running speeds, four points 3, 4, 5 and 6 are observation points which are transversely 1m away from the central axis of the two rails and are positioned on the same cross section, and a noise detection instrument is often placed at the position which is transversely 1m away from the central axis of the two rails for observation. In the vertical height, the distance between the measuring point 3 and the bottom surface of the steel rail is 0.976m, the distance between the measuring point 4 and the bottom surface of the steel rail is 0.576m, the distance between the measuring point 5 and the bottom surface of the steel rail is 0.176m, namely the height of the top surface of the steel rail, and the distance between the measuring point 6 and the bottom surface of the steel rail is 0.088m, namely the height of the waist surface of the steel rail. The two observation points 7, 8 are the longitudinal rail base level 0.176m, i.e. at the height of the rail top surface, and the observation point 5 is also in this plane. The horizontal distance of the observation point 7 is 7.5m away from the central axis of the two rails, and the observation point and the ring evaluation point 1 are on the same vertical plane; the horizontal distance of the observation point 8 is 1.5m away from the rail, and the observation point and the ring evaluation point 2 are on the same longitudinal plane; the observation points 5, 7 and 8 form a group of points for observing the change condition of the measuring point noise of the transverse section at different train running speeds.
Fig. 7 and 8 are graphs showing the weighted sound pressure level changes of the vibration noise a with the frequency at different train running speeds of the ring evaluation points 1 and 2. Overall analysis shows that the overall trends of the measuring points 1 and 2 are the same, and both show that the highest peak value of the vibration noise a weighted sound pressure level gradually increases from the zero point of the vibration noise a weighted sound pressure level of low frequency to the frequency of about 1000Hz, and thereafter, the a weighted sound pressure level value continuously decreases with the increasing frequency, and the decreasing rate is higher than the increasing rate in the past as can be seen from the figure. On the whole trend, the influence of the change of the train running speed on the train running speed is small, and on the contrary, compared with two measuring points, the influence of the distance between the transverse distance and the steel rail on the whole trend is larger.
Fig. 9 reflects the sound pressure level of the vertical plane vibration noise in the wheel track area of the train at the running speed of 350km/h, and observation points 3, 4, 5 and 6 are selected, so that the highest peak value of the sound pressure level of the vibration noise is shown from the sound pressure level of the low-frequency vibration noise to the sound pressure level of the vibration noise with the frequency of about 2400Hz in the overall trend, and the sound pressure level value of the noise is continuously reduced along with the continuous increase of the frequency. And the sound pressure level difference value between the two sound pressure levels has no great change, and the overall curves are relatively close.
Fig. 10 reflects the wheel-rail area transverse plane vibration noise analysis, where the transverse plane of the wheel-rail area vibration noise analysis at the running speed of 350km/h of the train is selected to be a plane flush with the rail top surface, the observation points 5, 7, and 8 are selected, and the overall trends among the measurement points are analyzed on the whole, and are all gradually increased from the zero point of the vibration noise sound pressure level of low frequency to the highest peak value of the vibration noise sound pressure level, and then the sound pressure level value is continuously decreased with the continuous increase of the frequency.
The method comprises the steps of analyzing the frequency domain characteristics of aerodynamic noise of a wheel rail area, selecting aerodynamic noise observation points of the wheel rail area to be consistent with the observation points of the vibration noise for the convenience of observation and the convenience of comparison of the noise change conditions of the vibration noise and the aerodynamic noise in the wheel rail system area, and researching the wheel rail near-field aerodynamic noise of the wheel rail system at the running speed of trains of 200km/h, 250km/h, 300km/h and 350 km/h.
Fig. 11 and 12 are graphs reflecting the weighted sound pressure level changes of the aerodynamic noise a with frequency at different train running speeds of the ring evaluation points 1 and 2. From the trend of the whole curve, the whole trends of the measuring points 1 and 2 are the same, and both show that the weighting sound pressure level of the vibration noise A with low frequency is firstly increased to the highest peak value of the weighting sound pressure level of the pneumatic noise A with certain frequency, and then the weighting sound pressure level value of the weighting A is continuously reduced along with the continuous increase of the frequency. And as can be seen from fig. 11 and 12, similar to vibration noise, the rate of decrease is greater than the previous rate of increase, and the trend of the a-weighted sound pressure level at different speeds is very similar.
Fig. 13 reflects the sound pressure level of the vertical plane vibration noise in the wheel track area of the train at the running speed of 350km/h, observation points 3, 4, 5 and 6 are selected, in terms of the overall trend, the aerodynamic noise in the wheel track area is the highest peak value of the sound pressure level in the low frequency area, then the sound pressure level of the aerodynamic noise is slowly attenuated along with the increase of the frequency, and the measurement points 3, 4, 5 and 6 all present the rule. And the sound pressure level difference between the two sound pressure levels has no great change, and the overall curves are relatively close.
Fig. 14 shows the vibration noise analysis of the transverse plane of the wheel rail area, where the transverse plane of the vibration noise analysis of the wheel rail area at the running speed of 350km/h of the train is selected to be a plane flush with the rail top surface, the observation points 5, 7, and 8 are selected to be analyzed integrally, and the overall trends among the measurement points are relatively the same, namely that the highest peak value of the sound pressure level of the aerodynamic noise is already present at low frequency, and then the highest peak value is gradually reduced along with the increase of the frequency.
Fig. 15 shows the noise component ratio of vibration noise and aerodynamic noise statistics at point 1 in the wheel track region at a train running speed of 250km/h, and shows that the noise is mainly aerodynamic noise at low frequencies, the noise is mainly vibration noise at high frequencies, and the ratio of aerodynamic noise at high frequencies is extremely close to 0.
In summary, in the embodiment of the invention, by establishing the wheel-rail vibration finite element model of the ballastless track of the high-speed railway, the vertical and longitudinal transfer characteristics in the vibration frequency domain of the ballastless track can be analyzed by using the harmonic response analysis method; by carrying out Fourier transformation and one-third frequency multiplication transformation on the time domain response, the vibration characteristic of the ballastless track under the load action of the high-speed train can be further researched from the angle of the frequency domain; establishing a vibration noise analysis model of a wheel rail area of a ballastless track of the high-speed railway, and performing Fourier transform and one-third frequency multiplication transform on time domain response to obtain a frequency domain result of vibration noise for noise analysis; the method comprises the steps of establishing a pneumatic noise analysis model of a wheel rail area of the ballastless track of the high-speed railway, converting obtained time domain aerodynamic pressure into aerodynamic pressure under a frequency domain through FFT (fast Fourier transform), and performing Fourier transform and one-third frequency multiplication transform on the obtained aerodynamic noise to obtain sound pressure level of the aerodynamic noise for analysis, so that the joint analysis of the vibration and noise analysis of the wheel rail area of the high-speed railway is realized, the defects of the conventional single vibration, vibration noise or air noise characteristic analysis are overcome, and a more scientific and reasonable method is provided for the analysis of the vibration and noise of the high-speed railway.
Those of ordinary skill in the art will understand that: the figures are schematic representations of one embodiment, and the blocks or processes shown in the figures are not necessarily required to practice the present invention.
All the embodiments in the present specification are described in a progressive manner, and the same and similar parts among the embodiments are referred to each other, and each embodiment focuses on the differences from other embodiments. In particular, apparatus or system embodiments, which are substantially similar to method embodiments, are described in relative ease, and reference may be made to some descriptions of method embodiments for related points. The above-described embodiments of the apparatus and system are merely illustrative, and the units described as separate parts may or may not be physically separate, and the parts displayed as units may or may not be physical units, may be located in one place, or may be distributed on a plurality of network units. Some or all of the modules may be selected according to actual needs to achieve the purpose of the solution of the present embodiment. One of ordinary skill in the art can understand and implement without inventive effort.
While the invention has been described with reference to specific preferred embodiments, it will be understood by those skilled in the art that various changes and modifications may be made without departing from the spirit and scope of the invention as defined in the following claims. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (6)
1. A method for analyzing vibration and noise in a high-speed railway wheel rail area based on fluid-solid coupling is characterized by comprising the following steps:
calculating wheel-rail interaction force according to vibration admittances and combined roughness of wheels, steel rails and wheel rails of the high-speed railway, constructing a wheel-rail vibration noise combined prediction model based on fluid-solid coupling according to the wheel-rail interaction force, and predicting to obtain vibration noise of the wheels, the steel rails and the track slabs by using the wheel-rail vibration noise combined prediction model;
constructing a fluid domain model of a wheel rail area flow field, obtaining aerodynamic pressure in the flow field by using the fluid domain model, and simulating according to the aerodynamic pressure to obtain aerodynamic noise of the wheel rail area;
according to the vibration noise of the wheels, the steel rails and the track plate and the aerodynamic noise of the wheel rail area, performing sound source contribution analysis on the near-field noise and the far-field noise of the wheel rail area based on the fluid-solid coupling theory; the obtaining of the aerodynamic noise of the wheel track area according to the aerodynamic pressure simulation comprises the following steps:
constructing an air domain prediction model of the aerodynamic noise, introducing aerodynamic pressure in a flow field under a frequency domain into the air domain prediction model of the aerodynamic noise, and simulating to obtain aerodynamic noise of a wheel rail region;
the construction of the air domain prediction model of the aerodynamic noise comprises the following steps: selecting a turbulence model, selecting air by default for a fluid material, selecting corresponding flow surfaces at an inlet, an outlet, a bottom, an upper part and a boundary which are arranged in the prior art, and dividing grids, wherein the type of an inlet boundary condition selects a speed inlet, the speed is selected according to the actual driving speed, the type of an outlet edge selects a pressure outlet, on a symmetrical surface of the model, the type is selected and set as a symmetrical boundary, the types of boundary conditions on other surfaces are set as boundary surfaces which can not be passed by fluid, after the setting is finished, a pressure correction algorithm based on a pressure method is selected for solving, the calculation step length is selected according to 1/2 with the highest analytical frequency reciprocal, and a time domain result under the aerodynamic pressure in the flow field is obtained after the calculation is finished;
performing FFT on the time domain result under the aerodynamic pressure to obtain the aerodynamic pressure in the flow field under the frequency domain;
pneumatic pressure p in the frequency domain for each point i in the air domainiAerodynamic noise N from pointsiThe correlation between them is as follows:
2. the method of claim 1, wherein the method of calculating the vibrational admittances of the wheel, rail and wheel track comprises:
by applying a force F to a point j on the rail and wheel respectivelyjCalculating the displacement response D of the wheel and the steel rail at the loading point by using a harmonic response analysis methodjVibration admittance at wheel and rail loading points
The calculation was performed by the following formulas, respectively:
wheel-rail contact admittance alphacontactWheel-rail contact rigidity KcontactThe reciprocal of (a), namely:
αcontact＝1/Kcontact (3)。
3. the method according to claim 1, wherein the wheel-track vibration noise joint prediction model is modeled by selecting a ballastless track through finite element analysis software, a steel rail is simulated by using a three-dimensional solid unit, a fastener system is simulated by using a spring damping unit, a track plate is simulated by using a three-dimensional solid unit, the wheel-track vibration noise joint prediction model comprises a steel rail and a half track plate, and boundary conditions are simulated by applying symmetrical constraint at the middle part of the track plate and performing full constraint at the structural joint of the lower track plate.
4. The method according to claim 3, wherein constructing a fluid domain model of the wheel-rail region flow field comprises:
establishing a fluid domain model with the radius of 4.25m on the lowest axis of a symmetrical surface at one end of a foundation below a concrete base, completely removing a wheel body, a steel rail, a track plate, the base and the foundation below the base in the fluid domain by using Boolean operation, only leaving a pure fluid domain model, leading out the outer surface of the fluid domain model, carrying out grid division, and dividing the grid of the outer surface into an inlet surface, an outlet surface, symmetrical side surfaces, a top surface and a bottom surface, the minimum grid size of the inlet surface, the outlet surface and the symmetrical side surface is 0.01m, the grid type is triangular, the minimum mesh size of the top surface and the bottom surface is 0.5m, the mesh type is triangular, the minimum mesh size of the meshing of the air contact surfaces of the steel rail and the wheels is 0.01m, the mesh type is triangular, and the 3D body mesh division is performed based on the meshing of the outer surface of the fluid domain model and the meshing of the air contact surfaces of the steel rail and the wheels.
5. The method according to claim 1, wherein the performing the sound source contribution analysis on the near-field noise and the far-field noise of the wheel-rail region based on the fluid-solid coupling theory according to the vibration noise of the wheel, the steel rail, the track slab and the aerodynamic noise of the wheel-rail region comprises:
the near-field noise is obtained by extracting air pressure values at all nodes in the air domain and converting the air pressure values, the far-field noise is based on an algorithm of acoustic infinite elements and numerical interpolation, and the air pressure p corresponding to an infinite element grid unit j generated on the outermost surface of the air domain is obtained according to the calculation result of the near-field noisejThe calculation is carried out in such a way that,
obtaining the distance r from each point i in the region outside the air domain to the centroid position by setting the centroid position of a geometric body formed by an infinite element closed surface, and obtaining the corresponding air pressure p at the position i outside the air domain by selecting a proper infinite element boundary interpolation order n and calculating according to the following formulai：
6. The method according to claim 2, wherein the performing the sound source contribution analysis on the near-field noise and the far-field noise of the wheel-rail region based on the fluid-solid coupling theory according to the vibration noise of the wheel, the steel rail, the track slab and the aerodynamic noise of the wheel-rail region comprises:
for near-field noise analysis of a wheel track area, under the running speed of each train, 8 observation points are placed for observing the noise change value of the train, each observation point is provided with a microphone, and the 8 observation points are arranged beside a line; the measuring points 1 and 2 are based on the requirement of GB/T5111 plus 2011 for the placement of the position of an acoustic noise measurement microphone for the emission of a rail locomotive, the microphone is placed 7.5m away from a steel rail and 1.2m +/-0.2 m above the top surface of the steel rail, the observing points 1 and 2 are environment evaluation index measuring points, A weighting sound pressure levels at different train running speeds are respectively adopted for noise evaluation at two points, the four points of the measuring points 3, 4, 5 and 6 are observation points which are transversely 1m away from the central axis of the two rails and are positioned on the same cross section, on the vertical height, the measuring point 3 is 0.976m away from the bottom surface of the steel rail, the measuring point 4 is 0.576m away from the bottom surface of the steel rail, the measuring point 5 is 0.176m away from the bottom surface of the steel rail, namely on the height of the top surface of the rail, the measuring point 6 is 0.088m away from the bottom surface of the steel rail, namely on the height of the rail waist surface, and the measuring points 7 and 8 are two observation points 0.176m away from the bottom surface of the longitudinal steel rail, namely on the height of the top surface of the rail, the observation point 5 is also positioned on the plane, and the horizontal distance of the observation point 7 is 7.5m away from the central axis of the two rails and is on the same vertical plane as the ring evaluation point 1; the horizontal distance of the observation point 8 is 1.5m away from the central axis of the two rails, and the observation point and the ring evaluation point 2 are on the same vertical plane; the observation points 5, 7 and 8 form a group of points for observing the change condition of the measuring point noise of the transverse section at different train running speeds.
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